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BEST AVAILABLE COPY ww. 30j, w. mmm @522%1'? DALmna-Dmcs mm oct. so. 19553 4 sumssmt 2,

27j C) L26 BEST AVAiLABLE COPY @aired States @aterra BEST AvAnABLE coPY Patented Nov. 30, 1965 The invention relates to a valvelcss, hydraulic, pneumatic or hydro-pneumatic damping element, especially for shock-absorbers, shock-absorber legs, hydraulic or pneumatic springs and the like.

This damping'element can be so formed that it damps in one or both directions of movement, it being possible for the damping to be different for each direction.

If desired in such a damping element there can be installed an adjustingarrangement by which the intensity lof the damping can be set before commencement of operation or adjusted during operation.

In the known damping elements the damping is eiected -by one or more bores arranged in the damping piston,

which in order to achieve a varying damping in the two directions of movement are entirely or partially covered with valve spring discs. When a specific pressure of the damping medium is exceeded these discs lift themselves more or less away from the bores and thus clear a larger or smaller throttle cross-section, or they block oit a bore completely for the one direction of through-flow.

In order to avoid an irregular distribution of tension in the valve spring discscaused for example by the rolling or stamping operation in the production or by material fatigue on longer duration of operation-or in order to be able to adjust the desired initial tension at all, appropriate measures must be provided. Accordingly it is necessary to adjust every individual apparatus, for example a shock` absorber, exactly so. that it delivers the prescribed characteristics, it being necessary for a specific temperature yof the dampingmedium to be adopted as basis, since the viscosity or intensity of the medium and thus also the damping behaviour are temperature-dependent.

Now the present invention is based upon the problem of providing a damping element which does not possess the indicated drawbacks and furthermore is completely reliable in operation as a result of the absence of all movable parts, and renders possible a relatively cheap production. The stated problem is solved by a damping element which is characterised according to the invention by the following features, taken individually or combined with one another:

(a) A cylindrical flow chamber serving for the rearrangement of the tlow lines on reversal of the direction -of flow, into which chamber a channel opens tangentially and a central bore opens axially;

(b) Nozzles formed hydrodynamically or aero-dynamically in a manner known per se, the throttle resistance 'of which is greater in one direction of passage than in the other; f

(c) Combination of (a) and/or (b) with passages whose throttle resistance is the same in both vdirections of ow.

Thcdamping effect comes about due to the fact that the damping medium is introduced tangentially into the two flow chambers and there forms a more or less strong eddy in dependence upon the speed of llow. Due to this eddy formation the damping medium is forced away from the central bore as a result of the centrifugal force, so that a bathe effect dependent upon the speed of ow occurs, that is to say the damping action increases with increasing piston speed.

Experiments have shown that such damping elements display a largely constant damping behaviour, that is to say that they possess a nearly constant degree of damping both at low and at high temperatures,

If a damping action is desired in both directions, flow chambers can be arranged on both ends of the damping cylinder, which are connected with one another through one or more conduits which open tangcntially into the flow chambers and with the damping chamber by central bores in the transverse walls. Naturally in place of the conduits a jacket could be placed around the damping cylinder, in which case the uid is conducted in the annular space between the cylinder and the jacket.

According to a further form of embodiment of the invention the two eddy chambers can be housed coaxially in the damping piston, these chambers being connected with one another through a central channel and their tangential inlets connecting the end of the damping piston with the flow chamber in each case.

For thc inlluencing of the damping behaviour of the two flow chambers according to a further development of the invention a preferably axially adjustable hollow cylinder is arranged in place of the central connecting channel.

In order to be able to influence the speed of response as well as the damping behaviour of the flow chambers, the axially adjustable insert between the two flow chambers is advantageously so formed that its external diameter represents a multiple of the diameter of its central bore and also its axial length is greater than the thickness of the partition between the two flow chambers. By such an insert a large part of the damping medium is forced out of the centre of the flow chambers, so that the rcmainder of the medium contained in the flow chamber is situated at a relatively great distance from the centre that is to say is much more strongly influenced by thc centrifugal force, and furthermore comes more rapidly into rotation-in the case of tangential inflowsince tht mass to be accelerated is less than if the damping mediurr were to lill the entire ow chamber.

A further possibility of making the damping behaviour of the two ow chambers different from one another con sists in making the central connecting channel conical.

In order to achieve a quite particular damping be haviour in the damping element according to the inven tion the passages and/or nozzles can be entirely or par tially covered in a manner known per se by means c adjustable discs or by means of valve spring discs whic lift away due to the pressure of the damping medium.

In order to be able to set the damping behaviour a cording to the requirements in each case, according to further development of the invention the central bor: in the transverse walls of the flow chambers are provide with threadings into which externally threaded hollo cylinders are screwed, with which there are associated s1 stops, the counter-stops of which are arranged in a mai ner known per se on the damping piston. By the adjus ment of these hollow cylinders the damping behavior can be inuenced within wide limits, so that inaccuracil in production can be compensatcd subsequently. Furthe -more due to this arrangement it is possible to use oi and the name type of shock-absorber for different pu poses with different damping behaviours.

In order to prevent the hollow cylinders from enterii the damping chamber, they are cxpcdicntly provided their side facing the flow chamber with a collar-like e tension which also forms an additional means for the i fluencing of the degree of damping.

Furthermore between the internal threadings of t central bores and the external threadings of the hoilc cylinders there is advantageously provided a tougt elastic means, preferably in the form of a tube, whi

BEST AVAILABLE COPY serves to prevent undesired shiftingof the hollow cylinders.. According to the invention `furthermore according to the reqiurements `made in each case-one of the two transverse walls maybe omitted, the connecting conduits issuing tangentially from the flow chamber and opening into the damping chamber on the side opposite to the flow chamber. It can also be advantageous if the connecting `conduitsl are introduced into thel damping chamber at different levels. s

4The tlow cross-section of the central bore in the flow chamber can further be varied intermittently or steplessly by an adjusting element.

This adjustingelement advantageously consists of a rotatably mounted disc which processes at least one hole which is so arranged on the disc that hy the rotation thereof the central bore can be more or less covered. A possibility of finer adjustment is obtained if a plurality of piercings are provided on the rotatably mounted disc, the arrangement of which is made such that they are all intersected by a circle described about the centre of rotation of the disc, the individual piercings possessing different forms, for example fish bladder shape.

A similar adjusting effect can be achieved if the radial defining surface of the rotatably mounted disc is made of spiral form. In this case the spacing of the centre of rotation of the disc from the edge of the central bore should be selected according to the minimum radius of the disc.

A further advantageous possibility of adjustment is obtained if as adjusting element there is used an axially movable pin, the tip of which is made conical and which extends more or less deeply into the central bore according to the axial adjustability, and thus leaves free a more or less large annular gap.

In many eases it proves expedient to render the effect of the adjusting means dependent upon the speed of llow of the flow medium. According to a further development of the invention this is achieved due to the fact that before the central bore there is arranged a covering disc which is so resiliently mounted that its spacing from the central bore, and thus the ow resistance, varies in dependence upon the speed of ow of the through-owing medium.

In order to render possible satisfactory working of the damping element according to the invention, more especially in order to avoid breaking away of the liquid column, for example of damping oil, on the occurrence of relatively strong pressure surges which change their direction rapidly, and in order to prevent cavitation phenomena which have a very disadvantageous effect, it is necessary that the liquid damping medium shoud be subject to a filling pressure of at least atm. super pressure (70 p.s.i.g.) maintained by a gas cushion, and between the liquid and the vgas there is provided a separating element known per se, preferably a oating piston. The separating clement here serves for a double purpose, namely, firstly to maintain the predetermined minimum pressure, and secondly to prevent dissolving of the pressure gas in the damping liquid.

Where a gaseous damping medium is used, similar consideration, to the above apply as regards the minimum pressure. Here however the compression ratio must be taken into consideration, which for example in pneumatic springs is defined by the ratio of the cylinder volume with the recuperator fully extended to the cylinder volume with the recuperator fully retracted, there being understood by the recuperator a piston rod, a plunger piston or the like. Now it has appeared that the manner of operation of the damping element according tothe invention is most advantageous if in the case of a gaseous damping medium the arithmetic mean of initial pressure (recuperator completely extended) and final pressure (recuperator completely retracted) is greater than 75 atm. super pressure (1000 p.s.i.g.).

The invention is explained in greater detail hereinafter with reference to the purely diagrammatic drawings with the aid of a plurality of examples of use, where- FIGURE 1 shows a hydro-pneumatic shock-absorber wherein the damping element is arranged in the -bottom of the damping cylinder;

FIGURE 2 shows a cross-section along the line lI--II in FIGURE l; v

FIGURE 3 shows a hydro-pneumatic shockabsorber wherein the damping element is arranged in the damping piston;

FIGURE 4 shows a section through FIGURE 3 along the line IV-IV;

FIGURE 5 shows a longitudinal section through a shock-absorber;

FIGURE 6 shows a cross-sectiori along the line VI-VI in FIGURE 5;

FIGURE 7 shows a damping piston in sectional lateral view;

FIGURE 8 shows a section through FIGURE 7 along the line VIII-VIII;

FIGURE 9 shows the sectional lateral view of a damping piston with adjustable hollow cylinder;

FIGURE 10 shows a damping piston with adjustable cylinder in section;

FIGURE ll shows the arrangement of an adjusting element of disc form before the central bore of a ow chamber;

FIGURES l2 and 13 show forms of embodiment of such adjusting elements;

FIGURE 14 shows an adjusting element in the form of a pin with conical tip;

FIGURE 15 shows an adjusting device inuenceable by the speed of llow.

The damper internal cylinder 1 according to FIGURE l is surrounded by a second cylinder 2 at slight spacing, so that an annular space 3 is produced which is connected through bores 4 with the internal space 5 of the damper internal cylinder 1. A piston rod 6 introduced in pressure-tight fashion into this space 5 and carrying the piston 7 is made hollow on its side facing the piston 7, this cavity 3 being connected through a bore 9 in the damping piston 7 with the space 5. While the space 5 and the annular space 3 are filled with damping uid, in the cavity 8 in the piston rod 6 there is situated compressed gas which is closed off from the damping fluid by a floating piston 10. In the damping piston 7 there are provided passages for the damping fluid which according to the desired degree of damping can be cylindrical bores 11 or nozzles 12 with throttle resistance dependent upon the direction of flow. In the bottom of the shock-absorber there is arranged the damping element 13, the flow chamber 14 of which is connected with 'the space 5 through the central bore 15, while the channel 16, as may also be seen from FIGURE 2, constitutes the connection to the annular space 3 and opens tangentially into the flow chamber 14.

On driving in of the piston 7 the damping fluid is conducted out of the space 5 through the damping element 13 into the annular space 3 and returned through the bores 4 into the upper part of the space 5. In the case of this direction of ow the damping fluid in the damping clement 13 is opposed by a more or less constant throttle resistance, largely independently of the speed of flow.

In contrast thereto, on reversal of the direction of flow, that is to say in the extension of the damping piston 7, the dampingl fluid is introduced through the channel 16 tangcntially into the flow chamber 14 and thence issues through the bore 15 into the chamber 5. In dependence upon the speed of ow an eddy forms in the flow chamber 14, so that the damping fluid is forced as a result of centrifugal force away from the outlet bore 15. The action of the centrifugal force is the greater, the higher is the speed of flow with which the damping uid flows from the channel 16 into the iiow chamber 14. That is to say the quantity of fluid flowing through the bore 15 piston 27 and rises therewithf BEST AVAILABLE COPY is thesmalle'r, the greater upon -the-speed of lextension ofthe piston 7, in other words this signifies that the degree of damping ofthe rdamping element l13 vis 'a' functionof--thel-'spcedv of '-The' degree of damping-ofithedamping element 13;

allocated tothe individualspeeds of flow, can be adjusted within wide limits'fby variationof the individual dimensions thereof. Furthermore-the damping behaviour of the entire system can be influenced additionally by bores 11 and nozzles 12 possessingv athrottleresistance dependent upon the direction of flow,` which'can be arranged in the damping piston 7.

While in the example` of embodiment according to FIGURES'I and2 the-damping uid isfpumped back and forth by the damping piston 7-through the damping element 13, in the exampleofemb'odimentaccording to FIGURES 3 Aand 4, theA damping element 13 is arranged in the piston 7.` Inorderin'this example torender the degree of damping dependent upon the speed of extension of the damping-piston 7, theidamping element 13 must be so arranged that the channel 16 opening tangentially into the flow chamber 14 opens out of the damping piston 7 in theextendingdirection and the bore-15 opens out of the damping piston 7 in the retracting direction, so that in the former direction a greater throttle resistance occurs than in the latter.

For the maintenance of the internal pressure there is arranged at the bottom of the damping cylinder 1 a gas cushion 17 which is separated'from the damping fluid by a floating piston 18. Inthis example of embodiment again the degree of damping can be influenced by additional passages in the damping-piston 7, with or without throttle resistance dependent upon the direction of flow.

The dampingfluid can be replacedfor example in the case of pneumatic springs-by highly compressed gas. In this case obviously it is possible to dispense with the gas cushion 8 or 17 and the floating pistons 10 and 18. The above-described manner of operation remains however the same, although the damping element according to the purpose in each case must be somewhat differently designed, and the nozzles 12 are formed as diffusors, preferably after the style of Laval or Venturi nozzles.

In the case of the form of embodiment according to FIGURES and 6 the clamping cylinder 21 possesses on its two ends flow chambers 24 and 26 separated by transverse walls 22 and 23 from the damping space 25, which chambers are connected with one another through conduits 27 which open tangcntially into the flow chambers, while the connection between the ow chambers and the damping space is constituted by central bores 23 and 29 in the transverse walls 22 and 23.

The damping space 25 is divided into two spaces by a valveless piston 30 provided with a sealing ring 37. For the compensation of volume there is provided in the piston rod 38 of hollow formation a gas cushion 39, which is charged through the bore 40 in the damping piston 30 with the pressure of the damping medium and is separated therefrom by a floating piston 41. Into the central bores 28 and 29 of the transverse walls 22 and 23 there are screwed hollow cylinders 31 and 32 possessing set stops 33 and 34 on their sides facing the piston 30, while the counter-stops 35 and 36 are arranged on the damping piston 30. By means of these stops 33, 34, 35 and 36 the hollow cylinders 31 and 32 can be screwed more or less deeply into the flow chambers 24 and 26 according to the desired damping behaviour of the shock-absorber.

In place of the connecting conduits 27 as represented in the drawing there can be provided a second hollow cylinder surrounding the annular space. It is further possible to replace the conduits 27 by channels in or directly on the damping cylinder 1.

extension "of the In thedampingpiston 51 according to FIGURES 7 and -8,which'is secured on a piston rod 63 and possesses a scaling ring 64 on its cylindrical defining surface, there are coaxially arranged the flow chambers 52 and 53 which are connected with one another through a central chan nel 54 and possess tangential inlet channels 55 and 56, which connect the flow chambers 52 and 53 respectively with the end 57 and 58 respectively of the damping piston 51. It is generally sufficient to provide onesingle tangential channel per ow chambeqbut for example for reasons of ysymmetrical loading of the-'dampingpiston it can be expedient to provide a plurality of inlet channels inuniform distribution per flow chamber.

In order to be able lto influence the damping behaviour of the'ow chambers, in the example of embodiment according to FIGURE 9 in place of the central channel 54 there is arranged an axially adjustable hollow cylinder 59, by the adjustment of which the damping effect of the one chamber in'comparison with the other and thus the damping effect of the piston in retraction and extension can be made different.

In place of the hollow cylinder 59'in the example of embodiment according to FIGURE l0 there is provided a cylinder 60 which possesses a central bore 61 for the connection of the two flowy chambers 52 and 53 and like the hollow cylinder 59 is made axially adjustable. This adjustment can take place in both cases in a manner known per se, for example by means of a box Spanner or another suitable device. The dimensions of the cylinder 60 are advantageously so selected that its external diameter is a multiple of the diameter of the bore 61. The axial length of the cylinder 60 is so selected that it is greater than the thickness of the partition 62 between the two flow chambers 52 and 53.

It is self-evident that in place of the axially adjustable cylinders 59 and 60 there may also be provided nonadjustable cylindrical parts, especially in the case of damper pistons produced in large series, which are set from the outset in all details to a desired particular damping behaviour.

In the example of embodiment according to FIGURE ll in a shock-absorber piston 71 with the piston rod 72 there is arranged a flow chamber 73 which possesses a tangential channel 74 and an axial central bore 75. Furthermore in the damping piston 71 there are represented a nozzle 76 with throttle resistance dependent upon flow direction, and a bore 77 with throttle resistance which is equal in both directions of passage. Before the central bore there is arranged an adjusting element in the form of a rotatably mounted disc 78 having a piercing 79. By rotation of the disc 78 the piercing 79 can be brought more or less into coincidence with the central bore 75 and thus the passage cross-section can be varied.

FIGURE l2 shows an adjusting element in the form of a repeatedly pierced disc 80, the piercings 83, 84 and 85 of which possess different shapes and arc all intcrsected by a circle 82 described about the centre 81 of rotation of the disc 80. The centre of rotation 81 is more expediently so selected in relation to the axial bore 75 that its distance from the axis thereof is equal to the radius of the circle 82.

The example of embodiment according to FIGURE 13 shows an adjusting element 86 of disc form, the radial defining surface of which has a spiral course. Such an adjusting element is preferably to be so constructed, and its centre of rotation 87 is to be provided at such a distance beside the central bore 75, that its minimum radius just contacts the edge of the bore 75 and its maximum radius entirely covers the bore 75.

In FIGURE 14 there is provided as adjusting means an axially movable pin 88, the conical tip 89 of which extends intothe central bore 75 of the flow chamber 73 according to the adjustable depth of penetration of tht tip 89 amore or less large annular gap is left free for tht passage of the flow medium.

chamber 7 3` thatl the distance between .the lelement ,9d and l the bore -75 is variedby the inuence-ofthetlow'medium against the 4resistance-ot'th'e spring .91. The initial tension of the spring 91 andthussthaminim'um spacing of the dise90 can be regulated byfa setscrew92, which is arranged vatmthe end of' .the11supp'ort l.rod'93 conducted through a bore `of the'pistonrod-72."'In the case of this arrangementtheadjusting'v element .9 0 :forms a constant flowrcsistan'ce for the flow-,of mediumissuing from the l owlchamber'73 thrdugh-tliecentral Ibore'75. lFor the medium flowing into theiflowchamberi-nthroughthe central bore 75 the' resistance causedby-theadjusting element. 90 varies according ytothe speed of flow 4with which the med-lum strikes thereon, adjusting it against the action of'thc spring 91. v .i Byvthe above-described measures it'isp'ossible to ada-pt a standard damping element to`the`most various purposes with various requirements of thedampinglbehaviour.

I claim:

1. -A vdamping device 'comprising a piston device, a cylinder device contaningu'id and in which the piston device is movably located, means whereby the `uid can pass from-one side of the. piston to the'other, said means includingza'cylindrical ow chamber .provided with a tangential opening anda central 'bore opening whereby the fluid can tlow into either opening and'out of the other opening according to the direction of movement of the piston in the cylinder, and an adjustable element mounted adjacent said chamber to vary the rate of uid ow through said means, said adjustable element being a hollow control cylinder mounted adjustably in the central bore opening so that its depth of'entry into the tlow cham-ber can be varied.

2. A damping device as claimed in claim 1 where-in the adjustable hollow'cylinder' isfprovided with set stops, while a counter-stop is arranged on the piston.

3. A damping device comprisinga piston device, a cyl- BEST AVAILABLE COPY inder device including a damping space containing fluid' and in which the piston device is movably located, means whereby the fluid can pass from one side of the piston tothe other, said means including two cylindrical flow chambers, said ltlow chambers being arranged on both ends of the damping cylinder respectively, theilow cham-bers being connected with one another through at least one conduit which opens tangentially into the ow chambers, and with the damping space by central bores, where-by the uid can flow into either opening of cach tlow chamber and out of the other opening thereof according to the direction of movement of the piston in the cylinder, and an adjustable element mounted adjacent each chamber to vary the rate of `Iluid flow through said means.

4. A damping device as claimed in claim 3 wherein said adjustable damping element is in the form of a hollow control cylinder mounted adjustably in the central bore opening of each chamberfso that its depth of entry into the fiow chamber can be varied.

5. A damping device as claimed in claim 4, wherein the hollow cylinder has a collar-like extension on one side thereof.

References Cited by the Examiner UNITED STATES PATENTS 2,541,234 2/1951 Fulton 188--96 FOREIGN PATENTS 29,906 1912 Great Britain.

187,712 12/1905 Germany.

577,603 6/195s muy.

697,799 9/1940 Germany.

106,663 2/1943 Sweden.

356,840 6/1905 France.

993,852 ll/l95l France.

A HARRY LEVY, Primary Examiner.

EUGENE G. BOTZ, ARTHUR L. LA POINT,

Examiners.

x i. l, s 

1. A DAMPING DEVICE COMPRISING A PISTON DEVICE, A CYLINDER DEVICE CONTAINING FLUID AND IN WHICH THE PISTON DEVICE IN MOVABLY LOCATED, MEANS WHEREBY THE FLUID CAN PASS FROM ONE SIDE OF THE PISTON TO THE OTHER, SAID MEANS INCLUDING A CYLINDRICAL FLOW CHAMBER PROVIDED WITH A TANGENTIAL OPENING AND A CENTRAL BORE OPENING WHEREBY THE FLUID CAN FLOW INTO EITHER OPENING AND OUT OF THE OTHER OPENING ACCOPRDING TO THE DIRECTION OF MOVEMENT OF THE PISTON IN THE CYLINDER, AND AN ADJUSTABLE ELEMENT MOUNTED ADJACENT SAID CHAMBER TO VARY THE RATE OF FLUID FLOW THROUGH SAID MEANS, SAID ADJUSTABLE ELEMENT BEING A HOLLOW CONTROL CYLINDER MOUNTED ADJUSTABLY IN THE CENTRAL BORE OPENING SO THAT ITS DEPTH OF ENTRY INTO THE FLOW CHAMBER CAN BE VARIED. 